Pump or motor



Feb. 25, 1936, 5.4K. BENEDEK 2,032,079

PUMP OR MOTOR Original Filed April 25, 1932 2 Sheets-Sheet l yvg Feb. 25, 1936. E K, ENEDEK 2,032,079

PUMP OR MOTOR Original Filed April 25, 1932 2 Sheets$heet 2 ATTORNEYS Patented Feb. 25, 1936 UNITED STATES PATENT OFFICE Elek K. Benedek, Moun Original ap 607,409. Divided and her 20, 1933, Serial No 1 Claim.

This invention relates to reciprocating-pisto pumps or motors.

One object of my invention is to provide such a pump or motor with a simplified arrangement of the secondary rotor, piston crosshead guide blocks associated therewith, and pistons reciprocating in the primary rotor with their crossheads engaging the guide blocks to drivingly interconnect the two rotors.

Another object is to provide such a pump or motor with a solid rigid piston having a. solid rigid crosshead connected thereto.

Another object is to provide such a pump or motor with such a solid rigid piston and a solid 5 crosshead connected thereto, the crosshead having a continuous reaction surface thereon.

Another object is to provide such a pump or motor wherein a solid piston and a solid crosshead are integrally connected to form a rigid relatively inflexible unit.

Another object is to provide such a pump or motor with a piston and crosshead having a universal self-aligning connection therebetween, the latter in its preferred form being a ball-and socket connection.

Another object is to provide such a pump or motor with a solid and integral piston provided with a' ball portion which seats in a corresponding socket in the crosshead, this socket being preferably located eccentrically in the crosshead in order to provide a slight tilting thereof to form a wedge-shaped lubricant film.

This application is a division of application Serial No. 607,409, flled.April-25, 1932, now.Patent i No. 2,000,271, granted May 7, 1935. In the drawings:

Figure l is a central horizontal section of a form of pump embodying my invention.

Figure 2 is a vertical cross section taken through the plane of the pumping units of the pump shown in Figure 1. I

Figure 3 is a side elevation of a piston crosshead guide block thereof.

' Figure 4 is a central longitudinal section i through the piston crosshead guide block shown in Figure 3.

Figure 5 is a detail cross section of the piston crosshead guide block taken on the line 5-5 of Figure 4.

Figure 6 is a detail cross section taken on the line 66 of Figure 1. k

Figure 7 is a detail sectional view illustrating an alternative form of piston and crosshead unit.

Figure 8 is a detail sectional view of the unit shown inFigure 7, the section being taken in a t Gilead, Ohio, assignor to The Hydraulic Press Mfg. Gilead, Ohio, a corporation Company, Mount of Ohio plication April 25, 1932, Serial No.

his application Septem- 690,246

plane perpendicular to the plane of the section in Figure 7.

Referring to the drawings in detail, in the practical development of my improved pump, I provide a casing comprising a cylindrical shell or 5 ring 5 which is equipped with a supporting base 6, upper and lower slide guide pads l, and diametrically oppositely disposed hubs 8 apertured as shown to accommodate the usual eccentric or secondary rotor shifting rods. The usual drain 10 port 9 may also be provided.

The casing shell is closed at its ends by end casing plates l0 and II provided with centering shoulders l2 and secured as at i 3 to the respective ends of the casing ring.

Each end plate is provided with a recess H for receiving a ball race l5, and the plate I0 is equipped with a hub extension IS in which the enlarged head ll of the valve pintle I8 is secured by employment of a key or other suitable equipment. The hub It includes the usual combined intake and exhaust ports l9 and 20, each of which communicates with pintle cut-outs 2|, which cut-outs in turn communicate with upper and lower pairs of combined inlet and outlet bores respectively designated 22 and 23.

The portion of the pintle which projects into the pump chamber formed by the casing ring 5 and the end plates l0 and l I is provided with upperand lower valve cut-outs respectively des ignated 24 and 25 through which the inlet and exhaust bore pairs 22 and 23 may communicate suitably with the cylinder bores formed 'in the cylinder barrel or primary rotor, to be referred to in detail hereinafter. The portion of the pintle remaining after the forming of and between the cut-outs 24 and 25 provides a pintle bridge 26 which serves a purpose well understood in the art.

The casing end plate II is provided with a 4 bearing 21 for receiving the drive shaft section 28 wl..ch extends from the pump casing and to which power may be applied in any suitable manner. The portion of the drive shaft section projecting into the pump casing terminates in an 5 abutment head 29, and the cylinder barrel or primary rotor 30 is axially bored to receive the extended. end of the drive shaft section which carries said abutment head. The rotor 30 is also counter bored as at 3! to fit rotatably the portion of the pintle which projects into the pump casing, and in this manner an abutment shoulder 32 is formed against which the abutment head 29 is securely clamped by employment of a clamp ring 33 as shown in Figure 1 of the drawings. The

2 drive shaft section and the rotor 30 are also key 7 connected as at 34 for driving purposes.

' ing plates I0 and II, the rotor 30 half units.

The cylinder barrel or primary rotor 30 is in the nature of along rigid hollow cylindrical body and is reduced at its ends to receive ball race rings which cooperate with the previously described rings 15 and with ball bearings 35 interposed between said rings in the forming of antifriction bearings for said rotor. In a plane disposed centrally between the bearing rings 35 and likewise disposed centrally between the casis provided with a plurality, five being shown, of equidistantly spaced radial cylinder bores 31 which communicate through ports 38 with the pintle cut-outs 24 and 25.

A rigid single-piece shifter ring 39 is provided and is equipped with guide pads 40 for engaging the guide pads 1 of the casing, and suitable provision generally designated for connection with ordinary shifter rods or other suitable mechanical shifting equipment not shown. The ring is annularly recessed at its ends as at 42 to receive shoulder rings 43 which may be secured in position by set screws or other equipment as indicated at 44. Each keeper flange 45 and serves as a mounting for a ball race 45.

The eccentric or secondary the primary rotor,

These halves 41 are q pped with opposed annular recesses 48 which are concentric to the axis of rotation thereof.

The secondary rotor halves 41 also include laterally extending flanges 49 likewise concentric withrelation to the axis of rotation thereof, and on which are mounted race rings 5liewhich. with the rings 45 previously described and interposed rotor41 surrounds ball bearings 5|, provide anti-friction bearings for the secondary rotor with the shifter ring 35. It will be observed that the secondary rotor is centered on the plane of the primary rotor bores 31, and that the anti-friction bearings for the secondary rotor are disposed equi-distantly at each side of that central plane and within the anti-friction bearings for the primary rotor 34 previously described.

Between the eccentric or secondary rotor halves 41, individual guide blocks 52 are mounted, there being one guide block for each primary rotor cylinder bore, and the guide blocks are provided with arcu'ate ribs 53 which flt the annular recesses 48 of the secondary rotor halves, tangentially disposed grooveways 54 forming reaction faces 55, and inwardly directed openings for permit'ting freedom of movement of pistons 55 reciprocable in the-bores 31 of the primary rotor and which are connected with the secondary rotor by engagement of the integral plate crossheads 51- with which they are equipped in the grooveways 54 of the guide blocks. I

It will be observed that, by reason of the provision of the secondary rotor groove ways 48 and the guide block ribs 53, both being in concentric relation with the axis of rotation of the secondary rotor, said ribs and grooves or recesses will aflord primary reaction surfaces always concentric with the axis of rotation of the secondary rotor. In order absolutely to assure concentric 1613-! tion of the ribs of all of the guide blocks, I prefer to include in the manufacture of these blocks the turning of a laterally shouldered ring, a portion of which is disclosed in Figure 3 of the drawings, thus assuring perfectly coordinated reaction ribs and grooveways. After the has been shoulder ring includes a and comprises two plate-like block grooveways thus formed it may be severed by radial saw cuts as indicated in the said Figure 3 ad thereafter provided with the additional :grooveways and recesses which characterize the guide blocks.

The guide blocks are clamped between the secondary rotor plates or halves 41 by use of clamp screws or bolts 58 which pass through said flanges or halves 41 as illustrated in Figure 1 of the drawings. The screws 58 thus secure the secondary rotor halves and the guide blocks 52 together as a rigid rotor unit. Accordingly, the guide blocks abut or directly engage the clamp screws 58 as indicated at 59, and thus the screws serve not only to clamp the guide blocks between the secondary rotor half flanges, but also positively to secure them against end play.

It will be observed by reference to Figure 1 of the drawings that the spaced relation of the secondary rotor half flanges 41 provides an annular space within which the guide blocks 52 are mounted and in which lubricant will be impounded constantly to engage and provide flim bearing for the reciprocating cross heads 51. In order to assure this impounding of lubricant, a retaining shell 50 surrounds the rotor flanges 41 and the guide blocks 52 clamped therebetween and is secured as at iii to said flanges.

In Figures 7 and 8, I have disclosed an alternative piston and cross head construction in which the piston body proper is designated 52 and is a equipped with an extended portion shaped to form a ball head 53 adapted to flt a hemispherical recess or socket 54 extending well up into the body of the crosshead 65 and secured in the crosshead by employment of a sectional threaded ring 55 or 3 other suitable equipment. This ring 55 has a concavity engaging the ball head 53 and substantially forming an extension of the ball socket 54 beyond a hemisphere. Like the reaction face of the guide block which it is designed to oppose,

lubricant film bearing between them.

In the operation of my machine as a pump, when the primary and secondary rotors are positioned as shown in Figure 2 of the drawings,

'ing the purpose of building up a high pressure 5 with their axes of rotation coinciding, and power a is applied' through the drive shaft section 28, no reciprocation will be imparted to the pistons and crossheads. When the'eccentric or secondary rotor is shifted so'that its axis of rotation lies to one side or the other of the axis of the pintle, t

which-is the axis of rotation of the primary rotor, the pistons 55 will be caused to reciprocate radially in their bores '31, and the plate-like cr'oSS-. heads 51 will reciprocate tangentially in the guide 54, such piston reciprocation being occasioned by the relative movement. of which the rotors partake because -of their .oif center relation. The degree of reciprocation will,

of course, vary as the-degree of separation of the axes of rotation of the respective rotors varies. 1

It will be understood that I desire to comprehend within my invention such modifications as may be necessary to adapt itto varying conditions and uses.

Having this fully described my invention, what 1 ing a clearance over said crosshe'ads sufllclent to permit tilting thereot, each said crosshead being connected to each piston by a ball-and-socket Joint unit with one portion thereof on said piston and one portion on said crosshead, said ball portion being movable relatively to said socket portion during the operation of said pump or motor, the crosshead portion 0! said Joint unit being positioned eccentrically in said crosshead from front to rear thereof so as to cause said crosshead to tilt relatively to said guide block, whereby to provide a wedge-shaped clearance with a wedgeshaped lubricant iilm between said crosshead and said tangentially grooved guide block and also to 10 provide-selI-alignment between said piston and said crosshead.

ELEK x. BENEDEK. 

